Miter saw

ABSTRACT

A miter saw including a base, a turntable pivotably coupled to the base about a miter axis, and a miter angle lock assembly. The miter angle lock assembly includes a clamp biased into engagement with the base when in a clamped position, thereby exerting a clamping force on the base for locking the turntable relative to the base. The miter angle lock assembly further includes an override assembly for maintaining the clamp in a released position relative to the base in which the clamping force is released.

FIELD OF THE INVENTION

The invention relates to power tools, and more particularly to saws,such as miter saws, chop saws, etc.

BACKGROUND OF THE INVENTION

Miter saws are generally used for making miter cuts on workpieces. Inorder to make such a miter cut on a workpiece, the saw blade must beangularly adjusted to a desired miter angle relative to the base and theworkpiece. Typically, miter saws enable a user to angularly adjust thesaw blade to preset miter angles, such as 0°, 15°, 22.5°, 30°, and 45°.Once the saw blade has been adjusted to the desired miter angle, it isadvantageous to lock the saw blade in position in order to makeconsistent, repeatable cuts.

SUMMARY OF THE INVENTION

The invention provides, in one aspect, a miter saw including a base, aturntable pivotably coupled to the base about a miter axis, and a miterangle lock assembly. The miter angle lock assembly includes a clampbiased into engagement with the base when in a clamped position, therebyexerting a clamping force on the base for locking the turntable relativeto the base. The miter angle lock assembly further includes an overrideassembly for maintaining the clamp in a released position relative tothe base in which the clamping force is released.

The invention provides, in another aspect, a miter saw including a base,a turntable pivotably coupled to the base about a miter axis, and amiter angle detent assembly. The miter angle detent assembly includes anactuator and a bi-stable cam mechanism. The bi-stable cam mechanism isoperable to lock the turntable relative to the base at a desired miterangle by depressing the actuator a first instance, and is operable topermit relative movement between the turntable and the base about themiter axis by depressing the actuator a second instance.

The invention provides, in yet another aspect, a miter saw including abase, a turntable pivotably coupled to the base about a miter axis, amiter angle lock assembly, and a miter angle detent assembly. The miterangle lock assembly includes a clamp biased into engagement with thebase when in a clamped position, thereby exerting a clamping force onthe base for locking the turntable relative to the base. The miter anglelock assembly further includes an override assembly for maintaining theclamp in a released position relative to the base in which the clampingforce is released. The miter angle detent assembly includes an actuatorand a bi-stable cam mechanism. The bi-stable cam mechanism is operableto lock the turntable relative to the base at a desired miter angle bydepressing the actuator a first instance, and is operable to permitrelative movement between the turntable and the base about the miteraxis by depressing the actuator a second instance.

Other features and aspects of the invention will become apparent byconsideration of the following detailed description and accompanyingdrawings.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a front perspective view of a miter saw in accordance with anembodiment of the invention.

FIG. 2 is an exploded, top perspective view of a portion of the mitersaw of FIG. 1, illustrating a base, a turntable, a miter angle lockassembly, and a miter angle detent assembly.

FIG. 3 is an assembled, bottom perspective view of the portion of themiter saw of FIG. 2 with portions cut away, illustrating the miter anglelock assembly in an unlocked state.

FIG. 3A is an enlarged perspective view of a portion of the miter anglelock assembly of FIG. 3.

FIG. 4 is an assembled, bottom perspective view of the portion of themiter saw of FIG. 2 with portions cut away, illustrating the miter anglelock assembly in a locked state.

FIG. 4A is an enlarged perspective view of a portion of the miter anglelock assembly of FIG. 4.

FIG. 5 is an exploded perspective view of the miter saw of FIG. 1,illustrating the base, the turntable, and a miter angle detent assembly.

FIG. 6 is an assembled, side view of the miter saw of FIG. 1 withportions cut away, illustrating the miter angle detent assembly in anenabled state.

FIG. 7 is a side view of the miter angle detent assembly of FIG. 6moving from the enabled state toward a disabled state.

FIG. 8 is a side view of the miter angle detent assembly of FIG. 6 inthe disabled state.

FIG. 9 is a side view of the miter angle detent assembly of FIG. 6moving from the disabled state toward the enabled state.

Before any embodiments of the invention are explained in detail, it isto be understood that the invention is not limited in its application tothe details of construction and the arrangement of components set forthin the following description or illustrated in the following drawings.The invention is capable of other embodiments and of being practiced orof being carried out in various ways. Also, it is to be understood thatthe phraseology and terminology used herein is for the purpose ofdescription and should not be regarded as limiting.

DETAILED DESCRIPTION

FIG. 1 illustrates a miter saw 10 including a base 12, a turntable 14pivotably coupled to the base 12 about a miter axis A1, and a saw unit18 pivotably coupled to the turntable 14 about a bevel axis. The sawunit 18 includes a saw blade (not shown), a motor 24 for rotating thesaw blade, and an actuator (e.g., a trigger, also not shown) foractivating and deactivating the motor 24. The turntable 14, and portionsof the base 12, collectively define a workpiece support surface 28 uponwhich a workpiece may be placed for a cutting operation. The miter saw10 also includes spaced fence assemblies 30 positioned on opposite sidesof the saw blade against which the workpiece may be abutted during acutting operation.

The miter saw 10 further includes a miter angle scale 34 attached to thebase 12 that can be referenced by a user of the miter saw 10 to executea miter cut on a workpiece. The miter angle scale 34 indicates the miterangle, about miter axis A1, to which the saw unit 18 is adjustedrelative to the base 12. The miter angle scale 34 includes notches 36that align with corresponding notches 38 in the base 12. These notches36, 38 coincide with commonly used miter angles (e.g., 0°, 15°, 22.5°,30°, and 45°).

With reference to FIG. 2, the miter saw 10 further includes a miterangle lock assembly 42 for locking and unlocking the turntable 14 andthe saw unit 18 relative to the base 12 about the miter axis A1. Themiter angle lock assembly 42 includes a clamp 44 biased into engagementwith a portion of the base 12 when in a clamped position (FIGS. 4 and4A) for exerting a clamping force on the base 12, and an overrideassembly 46 for releasing the clamping force and maintaining the clamp44 in a released position (FIGS. 3 and 3A) relative to the base 12.Accordingly, when the clamp 44 is in the released position, theturntable 14 may be pivoted about the miter axis A1 relative to the base12 to any desired miter angle to perform a cutting operation on aworkpiece.

In the illustrated embodiment of the miter angle lock assembly 42, theclamp 44 includes opposed beveled surfaces 48 that selectively (andsimultaneously) engage, respectively, inverse-tapered surfaces 50defined on the turntable 14 and the base 12, respectively (FIGS. 3A and4A). As a result, when the clamp 44 is in the clamped position, thetapered surfaces 48 on the clamp 44 wedge against the inverse-taperedsurfaces 50 defined on the turntable 14 and the base 12, respectively,thereby creating friction between the turntable 14, the clamp 44, andthe base 12 that is sufficiently high enough to rotationally lock theturntable 14 to the base 12. Alternatively, the clamp 44 may alsoinclude features (e.g., knurls, ribs, etc.) on the tapered surfaces 48and the inverse-tapered surfaces 50 on the turntable 14 and base 12,respectively, may include like or different features for increasing theamount of friction that can be developed between the turntable 14, theclamp 44, and the base 12 upon application of the clamping force. Withreference to FIG. 2, the inverse-tapered surface 50 is annular andcoaxial with the miter axis A1, and is defined on an arcuate portion 51of the base 12 positioned behind the miter axis A1 (with the miter anglescale 34 attached to the base 12 in front of the miter axis A1 from theframe of reference of FIG. 1).

With reference to FIGS. 2-4A, the miter angle lock assembly 42 alsoincludes a housing 52 attached to the underside of the turntable 14(e.g., by fasteners) and a follower stud 54, which has a threaded rearend to which the clamp 44 is attached (e.g., by a nut 56) and a threadedfront end 66, and which is received in coaxial bores 58 in the housing52 (only one of which is shown in FIG. 2) for sliding movement therewithalong an axis A2 oriented transverse to the miter axis A1 (FIG. 3). Withreference to FIG. 2, the miter angle lock assembly 42 further includes acompression spring 60 positioned within a pocket 62 in the housing 52that is coaxially mounted with the follower stud 54 and an adjustableretainer (e.g., a washer 63 and nut 64) secured to the threaded frontend 66 of the follower stud 54. Accordingly, the spring 60 is capturedbetween a rear surface of the pocket 62 and the retainer which, whenadjusted (e.g., by rotating the nut 64), can change the preload of thecompression spring 60 and the magnitude of the resultant clamping forceexerted by the clamp 44. The threaded front end 66 of the follower stud54 protrudes from the forward-most of the bores 58 in the housing 52,the reason for which is described in detail below.

With reference to FIG. 2, the override assembly 46 includes an actuator(e.g., handle 68) pivotably coupled to the turntable 14, at a locationforward of the miter axis A1, about an axis A3 oriented transverse toboth the miter axis A1 and the clamp axis A2. The override assembly 46also includes a cam 70 pivotably coupled to the turntable 14 (via thehousing 52) about an axis A4 (FIG. 3A) parallel to the miter axis A1 andtransverse to the handle axis A3, and a linkage 72 (FIG. 2)interconnecting the handle 68 and the cam 70. Specifically, the linkage72 includes a threaded front end 74 to which a nut 76 having acylindrical pivot 78 is threaded, and the handle 68 includes paralleltabs 80 in which coaxial circular apertures 82 are defined in which thecylindrical pivot 78 is received. Because the pivot 78 is offset fromthe handle axis A3, limited pivoting movement of the handle 68 isgenerally transmitted to the linkage 72 as translation in oppositedirections 84, 86.

With reference to FIGS. 3A and 4A, the cam 70 includes a cam lobe 88 anda lever 90 coupled for co-rotation with the cam lobe 88 with which arear end 92 of the linkage 72 is coupled. In the illustrated embodimentof the override assembly 46, the cam lobe 88 and the lever 90 areintegrally formed as a single piece. Alternatively, the cam lobe 88 andthe lever 90 can be formed as separate components and coupled forco-rotation in any of a number of different manners (e.g., by usingfasteners, adhesives, an interference fit, etc.). With reference toFIGS. 3A and 4A, the cam 70 further includes a slot 94 disposed near ata distal end 96 of the lever 90 in which the rear end 92 of the linkage72 is slidably received. More specifically, when the linkage 72 istranslated forward along direction 84, the rear end of the linkage 92 isslidable within the slot 94 toward a front end of the slot 94 (FIG. 3A),whereas when the linkage 72 is translated rearward along direction 86,the rear end of the linkage 94 is slidable within the slot 94 toward arear end of the slot 94 (FIG. 4A). The clearance provided by the slot 94allows the generally translational movement of the linkage 72 to betransferred to the cam 70 as pivoting movement about the axis A4.

With reference to FIGS. 3A and 4A, the cam lobe 88 includes a low-liftportion 96 defining a first radial dimension between the axis A4 and anouter peripheral surface of the cam lobe 88, and a high-lift portion 98defining a greater, second radial dimension between the axis A4 and theouter peripheral surface of the cam lobe 88. The cam lobe 88 is slidablyengageable with a distal end 99 of the follower stud 54 which, asmentioned above, protrudes from the forward-most of the bores 58 in thehousing 52, and which is maintained in contact with the cam lobe 88 bythe compression spring 60. As a result, as the cam 70 pivots about theaxis A4 and contact between the distal end 66 of the follower stud 54and the cam lobe 88 transitions from the low-lift portion 96 to thehigh-lift portion 98, the follower stud 54 is displaced rearward againstthe bias of the compression spring 60. Likewise, as the cam 70 pivots inan opposite direction about the axis A4 and contact between the distalend 99 of the follower stud 54 and the cam lobe 88 transitions from thehigh-lift portion 98 to the low-lift portion 96, the compression spring60 rebounds and urges the follower stud 54 toward the cam lobe 88 inorder to maintain constant contact between the distal end 99 of thefollower stud 54 and the cam lobe 88. Because the clamp 44 is affixed tothe rear end of the follower stud 54, the clamp 44 is also displaced inunison with the follower stud 54 in response to pivoting movement of thecam 70.

In operation, the miter angle lock assembly 42 is user-manipulatablebetween an unlocked state in which an operator may freely adjust themiter angle of the saw unit 18 (FIG. 3A), and a locked state in whichthe saw unit 18 is maintained at a specific miter angle (FIG. 4A). Toadjust the miter angle lock assembly 42 from the unlocked state to thelocked state, an operator pivots the handle 68 about the handle axis A3from the generally horizontal orientation shown in FIG. 3 to the obliqueorientation shown in FIG. 4. As the handle 68 pivots, the linkage 72 istranslated rearward along direction 86, causing the cam 70 to pivotabout the axis A4 and the distal end 99 of the follower stud 54 to slidealong the cam lobe 88 from the high-lift portion 98 to the low-liftportion 96. As contact between the cam lobe 88 and the distal end 99 ofthe follower stud 54 transitions from the high-lift portion 98 to thelow-lift portion 96, the radial dimension of which is less than theradial dimension of the high-lift portion 98, the compression spring 60progressively rebounds and continues to urge the distal end 99 of thefollower stud 54 against the cam lobe 88. As the compression spring 60rebounds, the clamp 44 moves in unison with the follower stud 54. Thegap between the tapered surfaces 48 of the clamp 44 and theinverse-tapered surfaces 50 of the turntable 14 and the base 12,respectively, progressively narrows until the surfaces 48, 50 engage theclamp 44, thereby wedging against both the turntable 14 and the base 12(shown in FIGS. 4 and 4A). Thereafter, the clamping force exerted on theturntable 14 and base 12 by the clamp 44 creates friction between theturntable 14 and base 12, locking the turntable 14 relative to the base12 in a desired miter angle of the saw unit 18.

When an operator desires to adjust the miter angle of the saw unit 18,the handle 68 is pivoted from the oblique orientation shown in FIG. 4 tothe generally horizontal orientation shown in FIG. 3. As the handle 68pivots, the linkage 72 is translated forward along direction 84, causingthe cam 70 to pivot about the axis A4 and the distal end 99 of thefollower stud 54 to slide along the cam lobe 88 from the low-liftportion 96 to the high-lift portion 98. As contact between the cam lobe88 and the distal end 99 of the follower stud 54 transitions from thelow-lift portion 96 to the high-lift portion 98, the radial dimension ofwhich is greater than the radial dimension of the low-lift portion 96,the follower stud 54 is displaced rearward and the compression spring 60is progressively compressed. The spring 60, however, continues to urgethe distal end 99 of the follower stud 54 against the cam lobe 88.Because the clamp 44 moves in unison with the follower stud 54, as thecompression spring 60 is compressed, the magnitude of the clamping forceexerted on the turntable 14 and the base 12 by the clamp 44 is reduced.Eventually, a gap opens between the tapered surfaces 48 of the clamp 44and the inverse-tapered surfaces 50 of the turntable 14 and the base 12,respectively, permitting the miter angle of the turntable 14 to befreely adjusted relative to the base 12. The miter angle lock assembly42 may be used to secure the turntable 14 relative to the base 12 whenthe desired miter angle coincides with one of the notches 36 in themiter angle scale 34, or when the desired miter angle does not coincidewith one of the notches 36.

With reference to FIGS. 2 and 5, the miter saw 10 also includes a miterangle detent assembly 100 for positioning the turntable 14 and saw unit18 relative to the base 12 at specified miter angles coinciding with thenotches 36 in the miter angle scale 34. The miter angle detent assembly100 includes an actuator or lever 102 (FIG. 5) pivotably coupled to afront end of the turntable 14, a detent member 104 pivotably coupled tothe turntable 14 and having a distal end 106 selectively receivable inthe notches 36, and a bi-stable cam mechanism 108 interconnecting thelever 102 and the detent member 104. The lever 102 is depressible orpivotable about axis A3 between a first or “default” position (FIG. 6)and a second or “actuated” position (FIG. 7). The lever 102 is biasedtoward the default position of FIG. 6 by a compression spring 110.

Referring to FIG. 5, the bi-stable cam mechanism 108 includes a thrustbody 112, a cylindrical first cam member 114 moveable in response toactuation by the thrust body 112, and a second cam member 116 affixed tothe turntable 14 and engageable with the first cam member 114. Withreference to FIG. 6, the first cam member 114 is received within acorresponding shaped blind bore 118 in the thrust body 112, and thefirst cam member 114 includes two sets of cam surfaces 120 a, 120 bspaced about the cylindrical periphery of the cam member 114. The firstset of cam surfaces 120 a are located at the distal end of the cammember 114, and the second set of cam surfaces 120 b are angularlyoffset relative to the first set of cam surfaces 120 a. Furthermore, thesecond set of cam surfaces 120 b are axially inset from the distal endof the first cam member 114 and the first set of cam surfaces 120 a.Both sets of cam surfaces 120 a, 120 b are oriented at an oblique anglerelative to a rotational axis A5 of the first cam member 114, thesignificance of which is explained in further detail below. Withreference to FIG. 8, the first cam member 114 also includes sets of stopsurfaces 122 a, 122 b that are alternately positioned about theperiphery of the first cam member 114 that separate the cam surfaces 120a, 120 b from each other. The stop surfaces 122 a, 122 b are orientedparallel to the rotational axis A5 of the first cam member 114.

With reference to FIG. 6, the second cam member 116 includes a singleset of cam surfaces 124 spaced about the cylindrical periphery of thecam member 116 that are located at the distal end of the cam member 116,and a set of stop surfaces 126 adjacent the cam surfaces 124. Like thecam surfaces 120 a, 120 b, the cam surfaces 124 are oriented at anoblique angle relative to the rotational axis A5 of the first cam member114 and are parallel to the cam surfaces 120 a, 120 b. The set of camsurfaces 124 of the second cam member 116 selectively and alternatelyinterface with the first and second sets of cam surfaces 120 a, 120 b ofthe first cam member 114, as is described in further detail below.Furthermore, the stop surfaces 126 of the second cam member 116selectively and alternately interface with the first and second sets ofstop surfaces 122 a, 122 b of the first cam member 114, as is describedin further detail below.

As illustrated in FIG. 5, the thrust body 112 includes an opposed set ofradially inward extending protrusions 128 that are slideably receivedwithin corresponding slots 130 (only the upper of which is shown in FIG.5) in the second cam member 116. Forward ends of the protrusions 128 arealternately engageable with the sets of cam surfaces 120 a, 120 b on thefirst cam member 114 for rotating the first cam member 114 within thethrust body 112 at discrete angular increments (e.g., by 90 degrees) foreach instance that the lever 68 is depressed.

Referring to FIGS. 5 and 6, the miter angle detent assembly 100 alsoincludes a rod 130 pivotably coupled to the detent member 104 by anintermediate link 132. The first cam member 114 is axially retained tothe rod 130 by a retainer (e.g., a C-clip 134), yet is rotatablerelative to the rod 130. The rod 130, in turn, is constrained for axialmovement whereas the detent member 104 is constrained for pivotalmovement about a pin 136 defining an axis A6, which is parallel with thepivot axis A3 of the lever 102. As such, axial movement of the rod 130causes corresponding pivoting movement of the detent member 104 betweenan engaged position (FIG. 6), in which the distal end 106 of the detentmember 104 is receivable within one of the notches 36, and an overrideor disengaged position (FIG. 8), in which the distal end 106 of thedetent member 104 is removed from the notch 36 in which it was formerlyreceived and prevented from re-engaging any of the other notches 36 inthe miter angle scale 34. A torsion spring 138 (FIG. 5) is positionedbetween the detent member 104 and the turntable 14 for biasing thedetent member 104 toward the engaged position.

With reference to FIGS. 5 and 6, the miter angle detent assembly 100further includes a linkage, which includes another rod 140,interconnecting the lever 102 with the thrust body 112. Like the rod130, the rod 140 is constrained for axial movement in operation of themiter angle detent assembly 100. Accordingly, the thrust body 112translates with the rod 140 when the lever 102 is depressed and pivotedbetween the default position (FIG. 6) and the actuated position (FIG.7). By urging the lever 102 via the compression spring 110 toward thedefault position, the compression spring 110 correspondingly urges therod 140 and the thrust body 112 in a rearward direction toward the miterangle scale 34. In the illustrated embodiment of the miter angle detentassembly 100, the compression spring 110 is captured between adownwardly extending tab 142 on the turntable 14 and the thrust body 112which, in turn, is retained to the rod 140 by a retainer (e.g., a C-clip144).

In operation, the miter angle detent assembly 100 is user-manipulatableto selectively position the turntable 14 and saw unit 18 in a number ofcommonly used miter angles. Once the turntable 14 and saw unit 18 arepositioned in one of the miter angles coinciding with the notches 36 inthe miter angle scale 34, the miter angle lock assembly 42 may beengaged or placed in the locked state as described above to positivelylock the turntable 14 relative to the base 12 at the selected miterangle for executing a cutting operation. To reposition the turntable 14and saw unit 18 to another miter angle, the miter angle lock assembly 42is first disengaged or placed in the unlocked state as described above.Depending upon whether another commonly used miter angle or an uncommonmiter angle (i.e., a miter angle not associated with any of the notches36 in the miter angle plate 34) is desired, the miter angle detentassembly 100 may or may not be shifted from an engaged state in whichthe detent member 104 is receiveable in one of the notches 36 in themiter angle scale 34 (FIG. 6) to a disengaged state in which the detentmember 104 is removed from the notch 36 in which it was formerlyreceived and prevented from re-engaging any of the other notches 36 inthe miter angle scale 34.

For example, if another commonly used miter angle is desired, the miterangle detent assembly 100 may remain in the engaged state, and theoperator of the miter saw 10 needs only to apply a lateral force againstthe turntable 14 (at a location spaced from the miter axis A1) that issufficiently high enough to cause the distal end 106 of the detentmember 104 to slide out of the notch 36 in which it was formerlyreceived. In other words, because the distal end 106 of the detentmember 104 is tapered, a component of the reaction force applied to thetapered distal end 106 by the miter angle scale 34 is directed upward,thereby imparting a moment on the detent member 104 in acounter-clockwise direction from the frame of reference of FIG. 6(against the bias of the torsion spring 138) to slightly pivot thedetent member 104. This slight pivoting movement by the detent member104 is transferred to the rod 130 through the intermediate link 132,which in turn slightly displaces the rod 132 in a forward direction tounseat the C-clip 134 from the first cam member 114. The detent member104 only needs to pivot a slight amount until the distal end 106 canslide out of the notch 36. Thereafter, the distal end 106 is slidablealong the upper surface of the miter angle scale 34 until another of thecommonly used miter angles is approached, at which time the torsionspring 138 unwinds to pivot the distal end 106 of the detent member 104into the notch 36 coinciding with that particular miter angle. In thismanner, the turntable can be moved and stopped at each of the notches 36coinciding with commonly used miter angles until the desired miter angleis reached.

Should the operator desire to bypass more than one of the notches 36 inthe miter scale 34, or should the operator desire to reposition theturntable 14 into an uncommon miter angle, the miter angle detentassembly 100 may be shifted from the engaged state (FIG. 6) to thedisengaged state by pressing and releasing the lever 102 a firstinstance against the bias of the compression spring 110, which displacesthe rod 140 and the thrust body 112 forward and away from the miterangle scale 34 (FIG. 7). As the thrust body 112 is displaced relative tothe second cam member 116, the protrusions 128 slide against one of thesets of cam surfaces 120 a, causing the first cam member 114 to bedisplaced away from the miter angle scale 34 in unison with the thrustbody 112. Because the cam surfaces 120 a are oriented at an obliqueangle with respect to the rotational axis A5 of the first cam member114, the linear force imparted by the protrusions 128 upon the camsurfaces 120 a is divided into a linear component, which causes thedisplacement of the first cam member 114 described above, and atangential component, which imparts rotation to the first cam member 114simultaneously with its axial displacement. As a result, the first cammember 114 is rotationally incremented about the rod 130 (e.g., by 90degrees) to an orientation in which the first set of cam surfaces 120 aare engaged with the cam surfaces 124 of the second cam member 116, andthe stop surfaces 122 a are engaged with the stop surfaces 126 of thesecond cam member 116, thereby elongating the effective length of thenestled cam members 114, 116 (FIG. 8). Because the first cam member 114is axially retained to the rod 130 by the C-clip 134, the rod 130 isalso displaced away from the miter angle scale 34, pulling theintermediate link 132 (which undergoes both translation and rotationrelative to the turntable 14) and pivoting the detent member 104 in acounter-clockwise direction relative to the frame of reference of FIG. 7against the bias of the torsion spring 138 from the engaged position(FIG. 6) to the disengaged position (FIG. 8). Once the cam members 114,116 are oriented as shown in FIG. 8, the detent member 104 is maintainedin the disengaged position indefinitely, permitting the turntable 14 tobe freely pivoted relative to the base 12 about the miter angle A1without concern for the detent member 104 re-engaging any of the notches36 in the miter angle scale 34.

To return the miter angle detent assembly 100 to the engaged state, thelever 102 is pressed and released a second instance against the bias ofthe compression spring 110. This time, as the rod 140 and the thrustbody 112 are displaced away from the miter angle scale 34, theprotrusions 128 slide against one of the second sets of cam surfaces 120b, causing the first cam member 114 to be displaced away from the miterangle scale 34 in unison with the thrust body 112. Because the camsurfaces 120 b are also oriented at an oblique angle with respect to therotational axis A5 of the first cam member 114, the linear forceimparted by the protrusions 128 upon the cam surfaces 120 b is dividedinto a linear component, which causes the displacement of the first cammember 114 described above, and a tangential component, which impartsrotation to the first cam member 114 simultaneously with its axialdisplacement. As a result, the first cam member 114 is rotationallyincremented about the rod 130 (e.g., by another 90 degrees in the samedirection) to an orientation in which the second set of cam surfaces 120b are re-engaged with the cam surfaces 124 of the second cam member 116(as shown in FIGS. 9 and 5), and the stop surfaces 122 b are engagedwith the stop surfaces 126 of the second cam member 116, therebyshortening the effective length of the nestled cam members 114, 116.Thereafter, the torsion spring 138 is permitted to unwind and pivot thedetent member 104 in a clockwise direction relative to the frame ofreference of FIG. 9 from the disengaged position to the engaged position(FIG. 6). If at this time the detent member 104 is not aligned with anyof the notches 36 in the miter angle scale 34, the distal end 106 of thedetent member 104 is slidable along the upper surface of the miter anglescale 34 until one of the commonly used miter angles is approached, atwhich time the torsion spring 138 unwinds further to pivot the distalend 106 of the detent member 104 into the notch 36 coinciding with thatparticular miter angle.

Various features of the invention are set forth in the following claims.

What is claimed is:
 1. A miter saw comprising: a base; a turntablepivotably coupled to the base about a miter axis; and a miter angle lockassembly including a clamp biased into engagement with the base when ina clamped position, thereby exerting a clamping force on the base forlocking the turntable relative to the base, and an override assembly formaintaining the clamp in a released position relative to the base inwhich the clamping force is released.
 2. The miter saw of claim 1,wherein the miter angle lock assembly further includes a spring biasingthe clamp into engagement with the base.
 3. The miter saw of claim 2,wherein the miter angle lock assembly further includes a followerthrough which the clamping force is transmitted, and wherein theoverride assembly is operable to displace the follower and move theclamp to the released position against the bias of the spring.
 4. Themiter saw of claim 3, wherein the spring is coaxially mounted with thefollower.
 5. The miter saw of claim 4, wherein the follower includes afirst end proximate the override assembly and a second end coupled tothe clamp.
 6. The miter saw of claim 5, wherein the miter angle lockassembly further includes a retainer positioned between the spring andthe override assembly, and wherein the retainer is positioned along alength of the follower to preload the spring an amount sufficient toprovide the clamping force.
 7. The miter saw of claim 5, wherein theoverride assembly includes a cam lobe pivotably coupled to the turntableand engageable with the first end of the follower, and an actuator forpivoting the cam lobe relative to the turntable to displace thefollower.
 8. The miter saw of claim 7, wherein the override assemblyfurther includes a lever coupled for co-rotation with the cam lobe. 9.The miter saw of claim 8, wherein the override assembly further includesa linkage interconnecting the lever and the actuator.
 10. The miter sawof claim 9, wherein the actuator is pivotably coupled to the turntable,and wherein pivoting movement of the actuator is transferred by thelinkage to the cam lobe as pivotal movement.
 11. The miter saw of claim10, wherein the cam lobe is pivotable about a first axis parallel to themiter axis.
 12. The miter saw of claim 11, wherein the actuator ispivotable about a second axis transverse to both the miter axis and thefirst axis.
 13. The miter saw of claim 7, wherein the cam lobe includesa first portion defining a first radial dimension, wherein the cam lobeincludes a second portion defining a second radial dimension greaterthan the first radial dimension, and wherein the clamp is moved from theclamped position to the released position in response to contact betweenthe first end of the follower and the cam lobe transitioning from thefirst portion to the second portion.
 14. The miter saw of claim 13,wherein the clamp is moved from the released position to the clampedposition in response to contact between the first end of the followerand the cam lobe transitioning from the second portion to the firstportion of the cam lobe.
 15. The miter saw of claim 1, wherein the baseincludes an arcuate portion with which the clamp is engaged when in theclamped position.
 16. The miter saw of claim 15, wherein the arcuateportion includes an annular surface with which a first portion of theclamp is engaged when in the clamped position.
 17. The miter saw ofclaim 16, wherein the turntable includes a turntable surface with whicha second portion of the clamp is engaged when in the clamped position.18. The miter saw of claim 17, wherein engagement of the first andsecond portions of the clamp with the annular surface and the turntablesurface, respectively, occurs simultaneously.
 19. The miter saw of claim15, wherein the override assembly includes an actuator positionedproximate a front of the turntable.
 20. The miter saw of claim 19,wherein the arcuate portion and the actuator are positioned on oppositesides of the miter axis.